US20040119280A1 - Fluid coolant union - Google Patents
Fluid coolant union Download PDFInfo
- Publication number
- US20040119280A1 US20040119280A1 US10/732,759 US73275903A US2004119280A1 US 20040119280 A1 US20040119280 A1 US 20040119280A1 US 73275903 A US73275903 A US 73275903A US 2004119280 A1 US2004119280 A1 US 2004119280A1
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- US
- United States
- Prior art keywords
- seal
- union
- coolant
- chamfered
- rotating
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 239000002826 coolant Substances 0.000 title claims abstract description 77
- 239000012530 fluid Substances 0.000 title claims abstract description 32
- 238000007789 sealing Methods 0.000 claims abstract description 33
- 238000007667 floating Methods 0.000 claims abstract description 19
- 238000000926 separation method Methods 0.000 claims abstract description 9
- 238000006073 displacement reaction Methods 0.000 claims abstract description 7
- 238000005461 lubrication Methods 0.000 claims description 2
- 239000003921 oil Substances 0.000 description 9
- 239000000463 material Substances 0.000 description 7
- HBMJWWWQQXIZIP-UHFFFAOYSA-N silicon carbide Chemical compound [Si+]#[C-] HBMJWWWQQXIZIP-UHFFFAOYSA-N 0.000 description 5
- 229910010271 silicon carbide Inorganic materials 0.000 description 5
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 5
- 239000003595 mist Substances 0.000 description 4
- 230000000712 assembly Effects 0.000 description 3
- 238000000429 assembly Methods 0.000 description 3
- 238000010276 construction Methods 0.000 description 2
- 238000001816 cooling Methods 0.000 description 2
- 230000008878 coupling Effects 0.000 description 2
- 238000010168 coupling process Methods 0.000 description 2
- 238000005859 coupling reaction Methods 0.000 description 2
- 230000003993 interaction Effects 0.000 description 2
- 239000007788 liquid Substances 0.000 description 2
- 238000003754 machining Methods 0.000 description 2
- 230000002035 prolonged effect Effects 0.000 description 2
- OKTJSMMVPCPJKN-UHFFFAOYSA-N Carbon Chemical compound [C] OKTJSMMVPCPJKN-UHFFFAOYSA-N 0.000 description 1
- 244000208734 Pisonia aculeata Species 0.000 description 1
- 238000010521 absorption reaction Methods 0.000 description 1
- 230000009471 action Effects 0.000 description 1
- 230000000295 complement effect Effects 0.000 description 1
- 238000005553 drilling Methods 0.000 description 1
- 229920001971 elastomer Polymers 0.000 description 1
- 239000000806 elastomer Substances 0.000 description 1
- 238000001125 extrusion Methods 0.000 description 1
- 229910002804 graphite Inorganic materials 0.000 description 1
- 239000010439 graphite Substances 0.000 description 1
- 238000007689 inspection Methods 0.000 description 1
- 230000007774 longterm Effects 0.000 description 1
- 239000000314 lubricant Substances 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000013011 mating Effects 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 239000002861 polymer material Substances 0.000 description 1
- 238000004513 sizing Methods 0.000 description 1
Images
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
- B23Q—DETAILS, COMPONENTS, OR ACCESSORIES FOR MACHINE TOOLS, e.g. ARRANGEMENTS FOR COPYING OR CONTROLLING; MACHINE TOOLS IN GENERAL CHARACTERISED BY THE CONSTRUCTION OF PARTICULAR DETAILS OR COMPONENTS; COMBINATIONS OR ASSOCIATIONS OF METAL-WORKING MACHINES, NOT DIRECTED TO A PARTICULAR RESULT
- B23Q11/00—Accessories fitted to machine tools for keeping tools or parts of the machine in good working condition or for cooling work; Safety devices specially combined with or arranged in, or specially adapted for use in connection with, machine tools
- B23Q11/12—Arrangements for cooling or lubricating parts of the machine
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
- B23Q—DETAILS, COMPONENTS, OR ACCESSORIES FOR MACHINE TOOLS, e.g. ARRANGEMENTS FOR COPYING OR CONTROLLING; MACHINE TOOLS IN GENERAL CHARACTERISED BY THE CONSTRUCTION OF PARTICULAR DETAILS OR COMPONENTS; COMBINATIONS OR ASSOCIATIONS OF METAL-WORKING MACHINES, NOT DIRECTED TO A PARTICULAR RESULT
- B23Q11/00—Accessories fitted to machine tools for keeping tools or parts of the machine in good working condition or for cooling work; Safety devices specially combined with or arranged in, or specially adapted for use in connection with, machine tools
- B23Q11/10—Arrangements for cooling or lubricating tools or work
- B23Q11/1015—Arrangements for cooling or lubricating tools or work by supplying a cutting liquid through the spindle
- B23Q11/103—Rotary joints specially adapted for feeding the cutting liquid to the spindle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
- F16L27/00—Adjustable joints, Joints allowing movement
- F16L27/08—Adjustable joints, Joints allowing movement allowing adjustment or movement only about the axis of one pipe
- F16L27/0804—Adjustable joints, Joints allowing movement allowing adjustment or movement only about the axis of one pipe the fluid passing axially from one joint element to another
- F16L27/0808—Adjustable joints, Joints allowing movement allowing adjustment or movement only about the axis of one pipe the fluid passing axially from one joint element to another the joint elements extending coaxially for some distance from their point of separation
- F16L27/0812—Adjustable joints, Joints allowing movement allowing adjustment or movement only about the axis of one pipe the fluid passing axially from one joint element to another the joint elements extending coaxially for some distance from their point of separation with slide bearings
- F16L27/082—Adjustable joints, Joints allowing movement allowing adjustment or movement only about the axis of one pipe the fluid passing axially from one joint element to another the joint elements extending coaxially for some distance from their point of separation with slide bearings having axial sealing
Definitions
- the present invention relates to a fluid coupling union such as a fluid coolant rotating union having a secondary sealing assembly which provides a depressurized condition displacement of the floating seal members from one another to provide a pop-off or gap between the seal members when the cooling union is depressurized.
- Fluid coolant unions are used extensively in conjunction with machine tools in various high speed drilling and boring transfer operations, high speed machine tool spindles, and in various applications such as machining centers and flexible transfer lines.
- the rotating union is structurally arranged to conduct various types of coolants, such as water-based, oil-based, and air-based fluids into the machine tool spindle.
- coolants may be used without prolonged dry-run periods of operation of the coolant union.
- Coolant unions generally include conventional seal assemblies having a rotating seal member mounted to the end of the rotating rotor member, which seal member is axially aligned to engage a non-rotating complementary seal member which is mounted to an axially movable carrier member mounted within the housing.
- coolant unions have been developed to include structure which separates the rotating and non-rotating seal facings from one another when fluid coolant is not passing through the union.
- Such “pop-off” type unions may be biased by spring or diaphragm members. Such biasing members position the seal members apart from one another in the absence of the passage of fluid coolant passing through the union.
- coolant unions are complex and expensive to manufacture. Also, during start-up of such coolant unions, excessive amounts of the fluid coolant are permitted to pass through the enlarged gap separating the rotating and non-rotating seal facings.
- the present invention provides a novel fluid coolant union which utilizes chamfered seal faces on at least one of the non-rotating and rotating portion floating seal assembly facings of the coolant union.
- Such coolant unions permit the handling of multiple cooling media, such as water-based, oil-based, air-oil mist based and air-based coolants to be directed through the coolant union. Additionally, it has been determined that by chamfering the seal faces in accordance with the present invention, the handling of the multiple media with a single seal balance is permitted while controlling leakage for the water-based, the oil-based, the air-oil mist and the air-based media to minimum levels.
- the chamfered seal face of at least one of the floating seal assembly facings additionally permits the use in the seal faces of special silicon carbide based materials containing specific and various porous type structures that may contain known lubricants such as graphite to provide a self-lubricating property to the seal faces.
- the seal faces may contain a specific combination of silicon carbide based materials which provide different porous structures with respect to the coolant media when operating in a dry run condition.
- the PV (pressure ⁇ sliding velocity) limit of such specialized seal facing provides an increase in operating life for such seal facings as compared to the situation when the seal facings are not chamfered.
- the coolant union includes a secondary sealing assembly.
- the secondary sealing assembly provides a sealing arrangement for the union to prevent leakage forward between the floating seal assembly of the coolant union and the carrier member that are adapted for axial sliding movement within the passageway in the housing.
- This secondary sealing arrangement or assembly includes an annular groove radially extending around the inside surface of the union housing, with the annular groove containing an annular seal member.
- the annular seal member is a U-shaped seal member. This U-shaped seal member is positioned within the annular groove and includes an inside corner thereof chamfered.
- the U-shaped seal member is then chamfered and sized to structurally cooperate with a triangular shaped back-up ring configured and sized to provide the unfilled volume within the annular groove which, when pressurized, stores sufficient relative displacement of the floating seal faces from one another to create a micro pop-off or a minute separation of the seal faces when depressurization occurs.
- the radial interference fit between the chamfered U-shaped annular seal member, the enclosing housing and the floating seal is less that standard to provide for the necessary interaction of the U-shaped seal member and the floating seal to create a micro pop-off between the rotating and the floating seal facings. This is accomplished by chamfering the inside corner of the U-shaped seal member to a size in relation to the dimension of the triangular plastic back-up ring to provide an unfilled volume and permit freedom of movement of the U-shaped secondary seal member.
- the unfilled volume when pressurized, stores sufficient relative displacement of the floating seal members with respect to one another to create the pop-off or separation of the seal faces. This separation or gap between the seal faces is very small.
- the triangular back-up ring is comprised of a selected plastic material which provides a necessary combination with the chamfered U-shaped seal member.
- the chamfered U-shaped seal member and back-up ring provides the freedom of movement for the long term functioning of the secondary seal assembly without hang-up while permitting the adjustability of the position of the floating seal for variable axial locations of the rotor.
- the resultant fluid coupling union is simpler in construction because it does not require a spring-biased member or baffle member to provide separation of the floating seal faces and to provide contact of the seal faces during pressurization.
- FIG. 1 is a vertical section view of the fluid coolant union provided in accordance with the present invention, with the coolant union shown in its unoperated, unpressurized condition;
- FIG. 2 is a view similar to FIG. 1 showing the fluid coolant union in its operated, pressurized condition in accordance with the present invention
- FIG. 3 is an enlarged view of the portion of the secondary seal assembly in accordance with the present invention when the coolant union is in the unoperated, unpressurized condition;
- FIG. 4 is an enlarged view of the portion of the secondary seal assembly in accordance with the present invention with the coolant union shown in the operated, pressurized condition;
- FIG. 5 is a schematic cross-sectional view illustrating the chamfered U-shaped secondary annular seal member in accordance with the present invention.
- FIG. 6 is a schematic cross-sectional view of the triangular back-up ring member of the secondary seal assembly in accordance with the present invention.
- FIGS. 1 and 2 a rotating fluid coolant union 10 incorporating the novel sealing arrangement in accordance with the present invention.
- the fluid coolant union 10 is utilized to conduct a fluid coolant either in a liquid or gaseous state from a source of coolant (not shown) to a spindle of a machine tool and the like.
- the spindle could be a machine tool used in the various applications such as machining centers, flexible transfer lines or any environment where fluid coolants such as water-based, oil-based, air-oil mist based and air-based coolants may be used in conjunction with the fluid coolant union 10 .
- the fluid coolant union 10 is comprised of a rotor or shaft member 12 , coupled to an end cap or housing member 14 .
- the end cap or housing 14 provides a cylindrical housing for the fluid coolant union with the housing identified as reference numeral 14 .
- the cylindrical bore 16 of the housing 14 defines a seal chamber 15 which locates the seal assembly 18 within the coolant union 10 .
- the seal assembly 18 is comprised of a rotating seal member 20 which is mounted to the end 12 a of the stub rotor member 12 and a non-rotating seal member 22 mounted to the end of a carrier member 24 .
- the rotating seal member 20 is, preferably, a disc-shaped, one-piece silicon carbide member which provides a generally flat-shaped annular seal surface 20 a about an opening 21 through the center thereof.
- the non-rotating seal member 22 of the seal assembly 18 is also a generally flat disc-shaped member that is also, preferably, comprised of silicon carbide.
- the seal members 20 and 22 of seal assembly 18 may be comprised of various silicon carbide grades.
- the non-rotating seal member 22 includes an opening 23 therethrough and includes an annular seal surface 22 a .
- the non-rotating seal member 22 is mounted to an end 24 a of a carrier member 24 which is axially movable within the cylindrical bore 16 of housing member 14 .
- one of the annular seal surfaces 20 a and 22 a is chamfered to present a narrowed and reduced annular contact seal facing between the floating seal assemblies. It is preferred that the non-rotating seal face surface 22 a is the seal surface that is chamfered. The chamfered portion is shown as beveled portions 25 and 29 in FIGS. 1 and 2.
- the mating between seal surfaces 20 a and 22 a permits the handling of multiple media, such as water-based, oil-based, air-oil mist based and air-based fluid materials to be used without prolonged dry run conditions. As shown in FIGS.
- the fluid coolant union 10 in accordance with the present invention further includes a secondary seal assembly 26 to prevent leakage of the fluid coolant forwardly of the carrier 24 through the gap 27 between the outer surface of the carrier side wall 35 and the inner surface 17 of the cylindrical bore 16 of the housing member 14 .
- the secondary seal assembly 26 is comprised of a U-shaped annular sealing member 30 positioned within an annular groove 28 positioned within the inner surface 17 of the housing member 14 that engages the inner surface 17 of the housing member 14 and the outer surface 35 of the carrier member 24 .
- the U-shaped annular sealing member 30 of the secondary seal assembly 26 as shown in FIGS. 3, 4 and 5 is a modified U-shaped type annular seal. As shown in FIG.
- the U-shaped annular seal member 30 is positioned within the annular groove 28 within the housing member 14 .
- the lip members 31 and 32 and the foot connection member 33 (FIG. 5) of the annular seal substantially contact the inner and outer surfaces of the annular groove as well as the front surface or the side of the groove opposite the high pressure area, as shown in FIGS. 1 and 3.
- the U-shaped seal member is comprised of an elastomer type material and includes a chamfered diagonal cut 34 on the foot portion of the seal assembly 30 that is positioned toward the outer surface 35 between the carrier 24 and the cylindrical bore 16 of the housing member 14 .
- This chamfered cut is sized in relation to a triangular back-up ring 36 to structurally cooperate with the triangular back-up ring 36 (FIG. 6) to provide an unfilled volume which, when pressurized, stores sufficient relative displacement energy (FIG. 4) to the floating seal assembly to create a micro pop-off or separation of the seal faces 20 a and 22 a when the coolant union is depressurized, the condition as shown in FIG. 1.
- FIG. 6 represents a cross-section of the annular back-up ring 36 which is comprised of polymer material.
- This particular specialized plastic material provides a back-up ring that controls the absorption of moisture and controls the hardness of the material as well as controls the machineability of the back-up ring to permit the back-up ring 36 to be structurally arranged to occupy the space and volume within the chamfer cut in the inner wall of the U-shaped annular seal.
- the U-shaped secondary seal member 30 engages the annular back-up ring 36 to prevent the extrusion of the secondary seal into the gap. Because of the precise control of the gap distance between the floating seal assembly and the rotor assembly, a reduced amount of fluid coolant is permitted to pass between the annular seal surfaces 20 a and 22 a of the rotating and non-rotating seal members. The gap between the seal members when the coolant union 10 is in the unpressurized, unoperable condition is minimized and substantially limited because of the pull-back action on the non-rotating seal member during depressurization of the union.
- the secondary seal assembly provides a sealing function as well as a separation function of the floating seal assembly.
- the radial interference fit between the chamfered U-shaped annular seal 30 and the annular groove 28 within the housing member 14 permits the adjustable setting of the gap between the annular seal faces 20 a and 22 a .
- the interference fit is less than standard such that upon pressurization of the union, the chamfer on the annular seal 30 and the back-up ring provide a sufficient interaction or displacement energy to create the micro pop-off of separation when the union is depressurized.
- This permits the adjustment of the floating seal assembly 24 for variable axial locations of the stub rotor member 12 and permits the predetermined relocation and adjustment of the floating seal assembly 24 .
- the sealing arrangement is described with reference to a stub rotor member 12
- the stub rotor assembly may be contemplated to be a bearingless stub rotor member or may be a rotor assembly that is confined within fixed bearing structures. This permits the present invention to provide a wide range of operation through a coolant union from hundreds of RPMs to in excess of 40,000 RPMs.
Abstract
Description
- This application claims priority to provisional patent application No. 60/435,890, filed on Dec. 20, 2002.
- The present invention relates to a fluid coupling union such as a fluid coolant rotating union having a secondary sealing assembly which provides a depressurized condition displacement of the floating seal members from one another to provide a pop-off or gap between the seal members when the cooling union is depressurized.
- Fluid coolant unions are used extensively in conjunction with machine tools in various high speed drilling and boring transfer operations, high speed machine tool spindles, and in various applications such as machining centers and flexible transfer lines. In such applications, the rotating union is structurally arranged to conduct various types of coolants, such as water-based, oil-based, and air-based fluids into the machine tool spindle. Preferably, such coolants may be used without prolonged dry-run periods of operation of the coolant union. Coolant unions generally include conventional seal assemblies having a rotating seal member mounted to the end of the rotating rotor member, which seal member is axially aligned to engage a non-rotating complementary seal member which is mounted to an axially movable carrier member mounted within the housing.
- In existing prior art coolant union assemblies, when the union is operating in the pressurized condition the sealing surface of the non-rotating seal member is biased into engagement with the sealing surface of the rotating seal member by overcoming some type of spring or baffle diaphragm bias means which is designed to axially separate the seal members when in the non-pressurized dry-running condition. As the liquid or fluid coolant is passed through the coolant union, the coolant lubricates the contacting seal members to minimize wear between the members. When the condition is reached where the union is unpressurized and fluid coolant is not passing through the union, a “dry running” condition is achieved and the facing surfaces of the rotating and non-rotating seal members do not receive any lubrication. During this dry-running condition, the increased wear on the seal facings results in leakage about the seal facings which ultimately require replacement of one or both of the seal members. Such replacement of the seal facing and the rotor assembly are expensive and time consuming.
- To overcome the problems associated with dry-running, coolant unions have been developed to include structure which separates the rotating and non-rotating seal facings from one another when fluid coolant is not passing through the union. Such “pop-off” type unions may be biased by spring or diaphragm members. Such biasing members position the seal members apart from one another in the absence of the passage of fluid coolant passing through the union. However, such coolant unions are complex and expensive to manufacture. Also, during start-up of such coolant unions, excessive amounts of the fluid coolant are permitted to pass through the enlarged gap separating the rotating and non-rotating seal facings.
- The present invention provides a novel fluid coolant union which utilizes chamfered seal faces on at least one of the non-rotating and rotating portion floating seal assembly facings of the coolant union. Such coolant unions permit the handling of multiple cooling media, such as water-based, oil-based, air-oil mist based and air-based coolants to be directed through the coolant union. Additionally, it has been determined that by chamfering the seal faces in accordance with the present invention, the handling of the multiple media with a single seal balance is permitted while controlling leakage for the water-based, the oil-based, the air-oil mist and the air-based media to minimum levels. The chamfered seal face of at least one of the floating seal assembly facings additionally permits the use in the seal faces of special silicon carbide based materials containing specific and various porous type structures that may contain known lubricants such as graphite to provide a self-lubricating property to the seal faces. By utilizing chamfered seal faces, the seal faces may contain a specific combination of silicon carbide based materials which provide different porous structures with respect to the coolant media when operating in a dry run condition. Thus, by utilizing chamfered seal faces, it has been found that the PV (pressure×sliding velocity) limit of such specialized seal facing provides an increase in operating life for such seal facings as compared to the situation when the seal facings are not chamfered.
- In accordance with a further embodiment of the present invention, the coolant union includes a secondary sealing assembly. The secondary sealing assembly provides a sealing arrangement for the union to prevent leakage forward between the floating seal assembly of the coolant union and the carrier member that are adapted for axial sliding movement within the passageway in the housing. This secondary sealing arrangement or assembly includes an annular groove radially extending around the inside surface of the union housing, with the annular groove containing an annular seal member. Preferably, the annular seal member is a U-shaped seal member. This U-shaped seal member is positioned within the annular groove and includes an inside corner thereof chamfered. The U-shaped seal member is then chamfered and sized to structurally cooperate with a triangular shaped back-up ring configured and sized to provide the unfilled volume within the annular groove which, when pressurized, stores sufficient relative displacement of the floating seal faces from one another to create a micro pop-off or a minute separation of the seal faces when depressurization occurs.
- The radial interference fit between the chamfered U-shaped annular seal member, the enclosing housing and the floating seal is less that standard to provide for the necessary interaction of the U-shaped seal member and the floating seal to create a micro pop-off between the rotating and the floating seal facings. This is accomplished by chamfering the inside corner of the U-shaped seal member to a size in relation to the dimension of the triangular plastic back-up ring to provide an unfilled volume and permit freedom of movement of the U-shaped secondary seal member. The unfilled volume, when pressurized, stores sufficient relative displacement of the floating seal members with respect to one another to create the pop-off or separation of the seal faces. This separation or gap between the seal faces is very small.
- The triangular back-up ring is comprised of a selected plastic material which provides a necessary combination with the chamfered U-shaped seal member. By sizing the back-up ring to the unfilled volume of the chamfered U-shaped seal member, the chamfered U-shaped seal member and back-up ring provides the freedom of movement for the long term functioning of the secondary seal assembly without hang-up while permitting the adjustability of the position of the floating seal for variable axial locations of the rotor. The resultant fluid coupling union is simpler in construction because it does not require a spring-biased member or baffle member to provide separation of the floating seal faces and to provide contact of the seal faces during pressurization.
- The present invention consists of certain novel features and structural details hereinafter fully described, illustrated in the accompanying drawings, and particularly pointed out in the appended claims, it being understood that various changes in the details may be made without departing from the spirit or sacrificing any of the advantages of the present invention.
- For the purpose of facilitating and understanding the present invention, there is illustrated in the accompanying drawings a preferred embodiment thereof, from an inspection of which, when considered in connection with the following description, the invention and its construction and operation and many of its advantages will be readily understood and appreciated.
- FIG. 1 is a vertical section view of the fluid coolant union provided in accordance with the present invention, with the coolant union shown in its unoperated, unpressurized condition;
- FIG. 2 is a view similar to FIG. 1 showing the fluid coolant union in its operated, pressurized condition in accordance with the present invention;
- FIG. 3 is an enlarged view of the portion of the secondary seal assembly in accordance with the present invention when the coolant union is in the unoperated, unpressurized condition;
- FIG. 4 is an enlarged view of the portion of the secondary seal assembly in accordance with the present invention with the coolant union shown in the operated, pressurized condition;
- FIG. 5 is a schematic cross-sectional view illustrating the chamfered U-shaped secondary annular seal member in accordance with the present invention; and
- FIG. 6 is a schematic cross-sectional view of the triangular back-up ring member of the secondary seal assembly in accordance with the present invention.
- Referring now to the drawings wherein like numerals have been used throughout the several views to designate the same or similar parts, there is illustrated in the drawings a rotating
fluid coolant union 10 incorporating the novel sealing arrangement in accordance with the present invention. Thefluid coolant union 10, as shown in FIGS. 1 and 2, is utilized to conduct a fluid coolant either in a liquid or gaseous state from a source of coolant (not shown) to a spindle of a machine tool and the like. The spindle could be a machine tool used in the various applications such as machining centers, flexible transfer lines or any environment where fluid coolants such as water-based, oil-based, air-oil mist based and air-based coolants may be used in conjunction with thefluid coolant union 10. - The
fluid coolant union 10 is comprised of a rotor orshaft member 12, coupled to an end cap orhousing member 14. The end cap orhousing 14 provides a cylindrical housing for the fluid coolant union with the housing identified asreference numeral 14. Thecylindrical bore 16 of thehousing 14 defines aseal chamber 15 which locates theseal assembly 18 within thecoolant union 10. - As shown in FIGS. 1 and 2, the
seal assembly 18 is comprised of a rotatingseal member 20 which is mounted to theend 12 a of thestub rotor member 12 and anon-rotating seal member 22 mounted to the end of acarrier member 24. The rotatingseal member 20 is, preferably, a disc-shaped, one-piece silicon carbide member which provides a generally flat-shapedannular seal surface 20 a about an opening 21 through the center thereof. Thenon-rotating seal member 22 of theseal assembly 18 is also a generally flat disc-shaped member that is also, preferably, comprised of silicon carbide. Theseal members seal assembly 18 may be comprised of various silicon carbide grades. Thenon-rotating seal member 22 includes an opening 23 therethrough and includes anannular seal surface 22 a. Thenon-rotating seal member 22 is mounted to anend 24 a of acarrier member 24 which is axially movable within thecylindrical bore 16 ofhousing member 14. - Importantly, one of the
annular seal surfaces seal face surface 22 a is the seal surface that is chamfered. The chamfered portion is shown asbeveled portions seal surfaces annular seal surface 22 a of theseal assembly 18 is narrower than the width of the rotatingannular seal surface 20 a then theseal assembly 18 is more capable of operating in an unpressurized running dry run condition without significant damage to theseal members - The
fluid coolant union 10 in accordance with the present invention further includes asecondary seal assembly 26 to prevent leakage of the fluid coolant forwardly of thecarrier 24 through thegap 27 between the outer surface of thecarrier side wall 35 and theinner surface 17 of the cylindrical bore 16 of thehousing member 14. Thesecondary seal assembly 26 is comprised of a U-shapedannular sealing member 30 positioned within anannular groove 28 positioned within theinner surface 17 of thehousing member 14 that engages theinner surface 17 of thehousing member 14 and theouter surface 35 of thecarrier member 24. The U-shapedannular sealing member 30 of thesecondary seal assembly 26, as shown in FIGS. 3, 4 and 5 is a modified U-shaped type annular seal. As shown in FIG. 3, the U-shapedannular seal member 30 is positioned within theannular groove 28 within thehousing member 14. When theU-shaped seal member 30 is positioned within the annular groove, thelip members diagonal cut 34 on the foot portion of theseal assembly 30 that is positioned toward theouter surface 35 between thecarrier 24 and the cylindrical bore 16 of thehousing member 14. This chamfered cut is sized in relation to a triangular back-upring 36 to structurally cooperate with the triangular back-up ring 36 (FIG. 6) to provide an unfilled volume which, when pressurized, stores sufficient relative displacement energy (FIG. 4) to the floating seal assembly to create a micro pop-off or separation of the seal faces 20 a and 22 a when the coolant union is depressurized, the condition as shown in FIG. 1. - FIG. 6 represents a cross-section of the annular back-up
ring 36 which is comprised of polymer material. This particular specialized plastic material provides a back-up ring that controls the absorption of moisture and controls the hardness of the material as well as controls the machineability of the back-up ring to permit the back-upring 36 to be structurally arranged to occupy the space and volume within the chamfer cut in the inner wall of the U-shaped annular seal. - During the operation of the
coolant union 10 in the pressurized operating condition, the U-shapedsecondary seal member 30 engages the annular back-upring 36 to prevent the extrusion of the secondary seal into the gap. Because of the precise control of the gap distance between the floating seal assembly and the rotor assembly, a reduced amount of fluid coolant is permitted to pass between the annular seal surfaces 20 a and 22 a of the rotating and non-rotating seal members. The gap between the seal members when thecoolant union 10 is in the unpressurized, unoperable condition is minimized and substantially limited because of the pull-back action on the non-rotating seal member during depressurization of the union. Thus, the secondary seal assembly provides a sealing function as well as a separation function of the floating seal assembly. Because the gap is minimized in the unpressurized condition, a minimum amount of coolant is permitted to pass between this reduced gap during start up of the coolant union. The reduced amount of fluid coolant to pass between the annular seal surfaces 20 a and 22 a results in a cleaner operating and more efficient fluid coolant union. - Additionally, the radial interference fit between the chamfered U-shaped
annular seal 30 and theannular groove 28 within thehousing member 14 permits the adjustable setting of the gap between the annular seal faces 20 a and 22 a. This is because the interference fit is less than standard such that upon pressurization of the union, the chamfer on theannular seal 30 and the back-up ring provide a sufficient interaction or displacement energy to create the micro pop-off of separation when the union is depressurized. This permits the adjustment of the floatingseal assembly 24 for variable axial locations of thestub rotor member 12 and permits the predetermined relocation and adjustment of the floatingseal assembly 24. - While the invention is described with reference to a preferred embodiment, various modifications may be made without departing from the spirit and scope of invention as defined in the appended claims. For example, although the sealing arrangement is described with reference to a
stub rotor member 12, the stub rotor assembly may be contemplated to be a bearingless stub rotor member or may be a rotor assembly that is confined within fixed bearing structures. This permits the present invention to provide a wide range of operation through a coolant union from hundreds of RPMs to in excess of 40,000 RPMs.
Claims (12)
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
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US10/732,759 US7229102B2 (en) | 2002-12-20 | 2003-12-10 | Fluid coolant union |
US11/805,980 US7597360B2 (en) | 2002-12-20 | 2007-05-25 | Fluid coolant union |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US43589002P | 2002-12-20 | 2002-12-20 | |
US10/732,759 US7229102B2 (en) | 2002-12-20 | 2003-12-10 | Fluid coolant union |
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US11/805,980 Continuation US7597360B2 (en) | 2002-12-20 | 2007-05-25 | Fluid coolant union |
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US11/805,980 Expired - Lifetime US7597360B2 (en) | 2002-12-20 | 2007-05-25 | Fluid coolant union |
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Application Number | Title | Priority Date | Filing Date |
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US11/805,980 Expired - Lifetime US7597360B2 (en) | 2002-12-20 | 2007-05-25 | Fluid coolant union |
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US (2) | US7229102B2 (en) |
EP (1) | EP1431646B1 (en) |
JP (1) | JP4837250B2 (en) |
KR (1) | KR101186984B1 (en) |
AT (1) | ATE403104T1 (en) |
CA (1) | CA2453877C (en) |
DE (1) | DE60322498D1 (en) |
ES (1) | ES2311087T3 (en) |
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US20140035274A1 (en) * | 2012-08-03 | 2014-02-06 | Deublin Company | Rotary union with pressure controlled seal actuator |
US20200284384A1 (en) * | 2016-07-07 | 2020-09-10 | Oerlikon Metco Ag, Wohlen | Powder rotary feedthrough having a purge chamber |
CN114433923A (en) * | 2022-03-10 | 2022-05-06 | 纽威数控装备(苏州)股份有限公司 | Full-automatic right angle milling head of central play water of disconnect-type rotary joint |
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Citations (21)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2420104A (en) * | 1943-07-22 | 1947-05-06 | Maytag Co | Seal guard ring |
US2723136A (en) * | 1952-09-13 | 1955-11-08 | Deublin Co | Rotating union |
US3405959A (en) * | 1965-03-16 | 1968-10-15 | Filton Ltd | Fluid sealing means |
US3455566A (en) * | 1966-03-11 | 1969-07-15 | John W Hull | Fluid sealing arrangements |
US3765690A (en) * | 1971-01-21 | 1973-10-16 | Ato Inc | Composite seal |
US4201392A (en) * | 1979-04-16 | 1980-05-06 | Grant Oil Tool Company | High and low pressure seal |
US4281839A (en) * | 1979-04-16 | 1981-08-04 | Purex Corporation | Rotary face sealing apparatus |
US4296952A (en) * | 1979-07-30 | 1981-10-27 | Aeroquip Corporation | Rotary joint |
US4626003A (en) * | 1985-06-03 | 1986-12-02 | Fmc Corporation | Constant motion swivel seal assembly |
US4681327A (en) * | 1985-11-25 | 1987-07-21 | Societe Nationale D'etude Et De Construction De Moteurs D'aviation "S.N.E.C.M.A." | Compound seal with pressure equalization aperture |
US4817995A (en) * | 1987-02-06 | 1989-04-04 | Deublin Company | Rotating union with replaceable sealing assembly |
US4893823A (en) * | 1988-12-21 | 1990-01-16 | Greene, Tweed & Co. | Seal assembly |
US4976282A (en) * | 1989-04-12 | 1990-12-11 | Deublin Company | Coolant union with fluid actuated seal assembly |
US5071318A (en) * | 1990-01-22 | 1991-12-10 | Westinghouse Electric Corp. | Reactor coolant pump having improved dynamic secondary seal assembly |
US5174614A (en) * | 1991-07-03 | 1992-12-29 | Kaleniecki James F | Bearingless rotary mechanical fluid coupling |
US5269537A (en) * | 1992-10-13 | 1993-12-14 | Caterpillar Inc. | Composite radial seal |
US5577775A (en) * | 1995-02-07 | 1996-11-26 | Barco, A Division Of Marison Industries | Bearingless coolant union |
US5617879A (en) * | 1995-02-17 | 1997-04-08 | Deublin Company | Sealing arrangement for a coolant union having a floating seal assembly |
US5669636A (en) * | 1995-08-01 | 1997-09-23 | Deublin Company | Floating seal assembly for a bearingless coolant union having air rotation capability |
US6406065B1 (en) * | 1999-07-10 | 2002-06-18 | Gat Gesellschaft Fur Antriebstechnik Mbh | Rotary joint for alternating media |
US6709025B2 (en) * | 2000-02-17 | 2004-03-23 | Buchi Labortechnik Ag | Vapor lead-through system for a rotary evaporator, and a rotary evaporator |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB923013A (en) | 1961-01-30 | 1963-04-10 | Dowty Seals Ltd | Improvements relating to sealing devices |
AT368819B (en) | 1980-11-26 | 1982-11-10 | Wiener Kabel Metall | MONITORING DEVICE FOR THE MANUFACTURING OF CABLES |
EP0052689B1 (en) * | 1980-11-26 | 1984-07-25 | Firma Carl Freudenberg | Sealing for rods or pistons |
AT396006B (en) * | 1991-06-18 | 1993-05-25 | Voest Alpine Ind Anlagen | ARRANGEMENT FOR THE INTRODUCTION OF PRINT MEDIA IN AXES, WAVES OR THE LIKE. |
JPH09317967A (en) * | 1996-05-30 | 1997-12-12 | Ritsukusu Kk | Mechanical seal installation structure |
JP3423654B2 (en) * | 1999-11-24 | 2003-07-07 | 日本ピラー工業株式会社 | End contact type mechanical seal |
JP3517711B2 (en) * | 2000-11-09 | 2004-04-12 | 日本ピラー工業株式会社 | Seal ring for mechanical seal and mechanical seal using the same |
-
2003
- 2003-12-10 US US10/732,759 patent/US7229102B2/en not_active Expired - Lifetime
- 2003-12-18 KR KR1020030092831A patent/KR101186984B1/en not_active IP Right Cessation
- 2003-12-18 EP EP03257988A patent/EP1431646B1/en not_active Expired - Lifetime
- 2003-12-18 DE DE60322498T patent/DE60322498D1/en not_active Expired - Lifetime
- 2003-12-18 JP JP2003420409A patent/JP4837250B2/en not_active Expired - Lifetime
- 2003-12-18 ES ES03257988T patent/ES2311087T3/en not_active Expired - Lifetime
- 2003-12-18 AT AT03257988T patent/ATE403104T1/en not_active IP Right Cessation
- 2003-12-22 CA CA2453877A patent/CA2453877C/en not_active Expired - Lifetime
-
2007
- 2007-05-25 US US11/805,980 patent/US7597360B2/en not_active Expired - Lifetime
Patent Citations (21)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2420104A (en) * | 1943-07-22 | 1947-05-06 | Maytag Co | Seal guard ring |
US2723136A (en) * | 1952-09-13 | 1955-11-08 | Deublin Co | Rotating union |
US3405959A (en) * | 1965-03-16 | 1968-10-15 | Filton Ltd | Fluid sealing means |
US3455566A (en) * | 1966-03-11 | 1969-07-15 | John W Hull | Fluid sealing arrangements |
US3765690A (en) * | 1971-01-21 | 1973-10-16 | Ato Inc | Composite seal |
US4201392A (en) * | 1979-04-16 | 1980-05-06 | Grant Oil Tool Company | High and low pressure seal |
US4281839A (en) * | 1979-04-16 | 1981-08-04 | Purex Corporation | Rotary face sealing apparatus |
US4296952A (en) * | 1979-07-30 | 1981-10-27 | Aeroquip Corporation | Rotary joint |
US4626003A (en) * | 1985-06-03 | 1986-12-02 | Fmc Corporation | Constant motion swivel seal assembly |
US4681327A (en) * | 1985-11-25 | 1987-07-21 | Societe Nationale D'etude Et De Construction De Moteurs D'aviation "S.N.E.C.M.A." | Compound seal with pressure equalization aperture |
US4817995A (en) * | 1987-02-06 | 1989-04-04 | Deublin Company | Rotating union with replaceable sealing assembly |
US4893823A (en) * | 1988-12-21 | 1990-01-16 | Greene, Tweed & Co. | Seal assembly |
US4976282A (en) * | 1989-04-12 | 1990-12-11 | Deublin Company | Coolant union with fluid actuated seal assembly |
US5071318A (en) * | 1990-01-22 | 1991-12-10 | Westinghouse Electric Corp. | Reactor coolant pump having improved dynamic secondary seal assembly |
US5174614A (en) * | 1991-07-03 | 1992-12-29 | Kaleniecki James F | Bearingless rotary mechanical fluid coupling |
US5269537A (en) * | 1992-10-13 | 1993-12-14 | Caterpillar Inc. | Composite radial seal |
US5577775A (en) * | 1995-02-07 | 1996-11-26 | Barco, A Division Of Marison Industries | Bearingless coolant union |
US5617879A (en) * | 1995-02-17 | 1997-04-08 | Deublin Company | Sealing arrangement for a coolant union having a floating seal assembly |
US5669636A (en) * | 1995-08-01 | 1997-09-23 | Deublin Company | Floating seal assembly for a bearingless coolant union having air rotation capability |
US6406065B1 (en) * | 1999-07-10 | 2002-06-18 | Gat Gesellschaft Fur Antriebstechnik Mbh | Rotary joint for alternating media |
US6709025B2 (en) * | 2000-02-17 | 2004-03-23 | Buchi Labortechnik Ag | Vapor lead-through system for a rotary evaporator, and a rotary evaporator |
Cited By (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20060273579A1 (en) * | 2005-05-17 | 2006-12-07 | Deublin Company | Multi-media rotary union |
EP1724502A3 (en) * | 2005-05-17 | 2009-03-04 | Deublin Company | Multi-media rotating union |
US7815224B2 (en) | 2005-05-17 | 2010-10-19 | Deublin Company | Multi-media rotary union |
US20110001316A1 (en) * | 2005-05-17 | 2011-01-06 | Deublin Company | Multi-media rotary union |
US8047576B2 (en) | 2005-05-17 | 2011-11-01 | Deublin Company | Multi-media rotary union |
US20140035274A1 (en) * | 2012-08-03 | 2014-02-06 | Deublin Company | Rotary union with pressure controlled seal actuator |
US9133967B2 (en) * | 2012-08-03 | 2015-09-15 | Deublin Company | Rotary union with pressure controlled seal actuator |
CN103015910A (en) * | 2012-11-07 | 2013-04-03 | 齐迎春 | Rotating sealed drilling and reaming conversion device |
US20200284384A1 (en) * | 2016-07-07 | 2020-09-10 | Oerlikon Metco Ag, Wohlen | Powder rotary feedthrough having a purge chamber |
CN114433923A (en) * | 2022-03-10 | 2022-05-06 | 纽威数控装备(苏州)股份有限公司 | Full-automatic right angle milling head of central play water of disconnect-type rotary joint |
Also Published As
Publication number | Publication date |
---|---|
US7597360B2 (en) | 2009-10-06 |
CA2453877A1 (en) | 2004-06-20 |
JP2004205037A (en) | 2004-07-22 |
US20070228723A1 (en) | 2007-10-04 |
ES2311087T3 (en) | 2009-02-01 |
US7229102B2 (en) | 2007-06-12 |
JP4837250B2 (en) | 2011-12-14 |
KR101186984B1 (en) | 2012-09-28 |
CA2453877C (en) | 2012-12-18 |
KR20040055648A (en) | 2004-06-26 |
EP1431646A1 (en) | 2004-06-23 |
EP1431646B1 (en) | 2008-07-30 |
ATE403104T1 (en) | 2008-08-15 |
DE60322498D1 (en) | 2008-09-11 |
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